WO2008135122A1

WO2008135122A1 - Cardan joint for connecting shafts transferring torque, particularly for steering spindles and cardan shafts of motor vehicles

Info

Publication number: WO2008135122A1
Application number: PCT/EP2008/002591
Authority: WO
Inventors: Georg Maierbacher; Karl-Heinz Martini; Joachim Rothe; Steffen Jerye
Original assignee: SGF SüDDEUTSCHE GELENKSCHEIBENFABRIK GMBH & CO. KG
Priority date: 2007-05-04
Filing date: 2008-04-01
Publication date: 2008-11-13
Also published as: DE102007021057A1

Abstract

The invention relates to a Cardan joint (10) for connecting shafts transferring torque, particularly for steering spindles (72) and Cardan shafts of motor vehicles, comprising two joint forks (14, 16) that can each be connected to a shaft and each have a pair of bearing means, a joint part (12) disposed between the joint forks (14, 16) having two pairs of complementary bearing means defining two intersecting or skew joint axes (B1, B2), and a damping arrangement (50) disposed in the joint part (12) damping at least rotary vibrations, wherein the two joint forks (14, 16) are coupled to each other via the joint part (12) while interacting in pairs with the bearing means and complementary bearing means. According to the invention, the joint part (12) also comprises two segment pairs (20, 30), of which each segment (22, 24 and 32, 34) is formed separately and connected to a complementary bearing means, and two adjacent segments (22, 24 and 32, 34) each are coupled to each other via damping bodies (511, 512, 513, 514) of the damping arrangement (50), said damping bodies being deformable in the direction transversely to the joint axes (B1, B2).

Description

Cardan joint for connecting torque-transmitting shafts, in particular for steering spindles and cardan shafts of motor vehicles

5

The present invention relates to a universal joint for connecting torque-transmitting shafts, in particular for steering spindles and cardan shafts of motor vehicles, with two joint forks, which are each connected to a shaft and each having a pair of bearing means, a disposed between the joint forks Ge-o steering part with two pairs of complementary Bearing means, which define two mutually crossing or skewed joint axes, and at least a torsional vibration damping, arranged in the joint part damper assembly, wherein the two joint forks are coupled together under pairwise cooperation of the bearing means and complementary bearing means on the hinge part. 5

Cardan joints are commonly used in propeller shaft assemblies in which torques must be transmitted through a plurality of shafts that are not parallel to each other. Cardan joints are used in particular for cardan shafts / cardan shafts for transmitting steering forces or for transmitting the engine output torque in motor vehicles. Although conventional universal joints fulfill the task of transmitting torques between mutually angled shaft sections. However, both torsional vibrations and shocks in the wave direction are transmitted as it were. In the design of modern steering systems, on the other hand, an attempt is made, unwanted

5 dampen torsional vibrations and shocks to increase ride comfort. For this purpose, corresponding dampers are integrated in the prior art either in the shaft assemblies themselves or in the universal joints.

Such a solution is known, for example, from document DE 192 89 90 A1. This document describes a universal joint, in which the joint part arranged between the two joint forks is made of two mutually rotatable cranked pin bodies. The two mutually rotatable pin body support each other via rubber buffers from each other. Furthermore, they are held together by a central draw bolt. This can be a; Rotationality of the two pin bodies reach each other, which is damped by compression of the inserted rubber body. Due to the tension of the two pin body on the central pin is only a rotation of the both journal body relative to each other possible. Other relative movements are excluded.

For further prior art, reference is made to document DE 100 0 270 270 A1. This document follows the approach to include in the Geienkgabein mounted bushings for receiving the journals of the joint part with the interposition of damping layers in the yoke ends. However, this can result in difficult to predict voltage states that can lead to unwanted wobbling in practice. Furthermore, this may affect the joint function.

A similar solution is shown in document DE 26 01 026 A1. Again, the joint bushings are arranged in rubber sleeves in the yoke ends.

Finally, US Pat. No. 3,878,695 shows a solution in which the connection between a shaft section and the universal joint takes place via an elastomeric sleeve body. This is exposed to torsional vibrations as well as axial vibrations in each case a shear stress. Although damping of torsional and axial vibrations can be achieved with such a solution,

.0 but builds this solution is relatively large. In addition, the permanent loads applied to the elastomeric damping body lead to an increased risk of failure due to wear.

It is accordingly an object of the present invention to provide a universal joint of the type described above, which has a comparison with the prior art improved damping characteristics with respect to torsional and axial vibrations in a simple and space-saving design

This object is achieved by a universal joint of the type described above, o is provided in accordance with a first aspect of the invention that the hinge part comprises two pairs of segments, each segment is formed separately and connected to a respective complementary bearing means, and that respectively two adjacent segments are coupled to each other in the direction transverse to the hinge axes deformable damping body of the damper assembly. >

According to the invention, the joint part comprises two pairs of segments, each with separately formed segments. This means that the joint part in total at least has four segments that can be produced as separate parts. However, it is also conceivable to provide more than four segments per joint part, for example joint parts with eight segments.

In an alternative embodiment according to a second aspect of the invention it can be provided that in each case two segments of a segment pair are formed connected to one another via a connecting element. In this way, under the action of external forces, a relative movement of the segments substantially takes place between the segments of different segment pairs.

10

The complementary bearing means are mounted in both alternatives of the invention on the segments of the two pairs of segments, so that the hinge part is connected by the intermediary of the complementary bearing means with the hinge axes in the style of a conventional universal joint. Between the segments i5 deformable damping body are arranged, which allow a relative movement of two adjacent segments to each other. As a result, both torsional vibrations and axial vibrations can be compensated, as will be discussed in detail below.

An essential advantage of the present invention is that the entire damping effect can be achieved solely by the inventive design of the joint part arranged between the joint forks. This makes it possible to form the joint forks in a conventional manner. In addition, depending on the individual case, the joint part can be adapted to the particular application,

.5, for example, by providing a joint part with harder or less hard damping bodies. Even in the case of maintenance, for example, after a certain period of operation, the universal joint can be repaired by simply replacing the joint part again, without consuming assembly steps in the joint forks or even on the waves to be connected are required.

10

A development of the invention provides that each of the bearing means comprises a bearing pin and each of the complementary bearing means comprises a respective bearing pin receiving bearing opening. Furthermore, it may be provided with regard to the storage that it is formed in a bearing bush or in a roller bearing, which is in turn received in a segment. In this solution according to the invention, therefore, the joint part is provided with corresponding bearing openings in the respective segments, which then each insert one into the joint forks. brought up camp boats. The bearing pins are held on the joint forks either by threaded arrangements or by press fit.

An advantageous embodiment of the invention according to the first aspect provides - that the bearing pin variable in the joint! can be introduced, wherein in accordance with the position of the bearing pin in the yoke, the damper assembly of the joint part is radially prestressed. As a result, the bearing bolts can be screwed at different depths into the joint forks. Assuming that the bearing bolts engage with their axial end face via a bearing bush on a corresponding counter-end face in their associated segment, so it can thus adjust the position of the segments relative to the joint forks. In other words, this means that with a stronger screwing a bearing pin in the yoke in the direction of the center of the universal joint that segment in which engages the hinge pin, also relative to the yoke is further displaced towards the joint center. If the other segments are already coupled with hinge pins in a corresponding manner and their position relative to the joint forks is already determined thereby, the stronger screwing in of the first-mentioned hinge pin results in greater compression of the damping bodies between the affected segment and the adjacent segments. As a result, the bias in the damping bodies can be increased and thus their damping behavior can be influenced during operation by increasing the overall rigidity. Of course, an opposite setting is possible, with one or more hinge pins are unscrewed in the direction away from the joint center of the joint forks. In this case, the damping body can relax accordingly, so that the overall rigidity of the damper assembly can be reduced. Accordingly, a targeted adjustment of the damping properties is possible with this development of the invention.

A development of the invention provides that the bearing bolts have a sealing surface for sealing the bearing opening, in which they engage. This solution is particularly advantageous if the bearing opening is formed with lubrication grooves. Thus, an undesirable leakage of lubricants from the bearing assembly can be prevented. In addition, by sealing the bearing opening even a lifetime lubrication can be ensured.

An embodiment of the invention provides that the joint part is disc-shaped and divided into at least four segments or two pairs of segments, wherein between opposite end faces of two adjacent segments at least one damping body is arranged. The damping body can be formed as separate elements. Preferably, however, it is provided that the damping bodies are interconnected. In this context, it can also be provided that the damping bodies are made of an elastic material, preferably of rubber.

In order to provide a dimensionally stable, as a unit manageable joint part, which offers a long service life with simple and cost-effective production, lo provides a development of the invention that the damping body are vulcanized to the end faces of the segments. Thus, for example, the segments can be made of a hard plastic material or metal, which are then placed in a mold and at least partially encapsulated with a rubber material. In a subsequent step, the rubber material can then be vulcanized so that it adheres to the segments and connects them to the joint part.

As already indicated above, the individual segments or segment pairs can be displaced relative to each other. In particular in order to counteract overload conditions which lead to an undesired failure of the gimbal according to the invention.

Lead 20 joints, may be provided according to a development of the invention that the segments have raised abutment surfaces with respect to their end faces. Such stop surfaces serve, for example, to provide a stop for adjacent segments in the case of high torques. As a result, the damping body arranged between these only one

> 5 predetermined maximum load - be it a compressive load or a tensile load - exposed, but they are also protected against a load due to the supporting contact with each other corresponding stop surfaces.

Furthermore, the end faces of the segments in a region may have a concave: o curvature. The damping bodies arranged therebetween can be adapted in their shape such that they have corresponding contact surfaces in this region for engagement with the end faces of the adjacent segments. Such a design of the damping body is due to the accumulation of material in this area of the targeted adjustment of the deformation behavior, in particular 5 to achieve a progressive deformation behavior of the damping body. In a basic form of the invention, only one damping body is arranged between two adjacent segments which, depending on the material properties, then exhibits a specific deformation behavior under a compressive load and in the case of an opposing tensile load. As already experienced above, this can be

5 Deformationsverhalteπ also influence by a suitable choice of bias. Another possibility for the targeted adjustment of the deformation behavior, in particular for achieving a progressive deformation behavior, is, for example, that between two opposite end faces of two adjacent segments each a flat insert part is provided, and lo that the insert part via a respective damping body with the end faces facing it connected is. This feature is particularly advantageous when the insert part extends into the clear gap between the abutment surfaces already mentioned above. Is compressed as a result of a certain load level of the damping body on both sides of the insert part so strong that the

Apply L5 stop surfaces to the insert part, so the damping body between the two adjacent segments and the insert part are so to speak shorted. The power transmission from one segment to the other then takes place only via the insert part, with substantially only its rigidity being decisive for the damping behavior as a result. So it is, then, if that is

.0 Dämpfungskörpersystem seen from two damping bodies and arranged between these insert part with different stiffnesses, a progressive characteristic obtained. This has a kink on when the abutment surfaces bear against the insert part, wherein the slope of the characteristic increases when the kink is exceeded, that is to say as the load increases. It is understood that ever

5 of the material properties for damping body and insert part of this behavior and the course of the characteristic are adaptable to the particular application.

Also, by a multi-layered damping system between two) adjacent segments, for example, by arranging several inserts with different stiffness, the damping behavior can be further adjusted as desired.

A development of the earth finding provides that the between the segments on; ordered insert parts, preferably to a deposit cross, are integrally connected to each other. As a result, in particular the manufacturability of the joint part can be improved. For example, the inlay cross can be used for injection and vulcanization. siervorgang better handle as a one-piece component, especially with regard to the fact that this is not undesirable in the mold during the injection process.

In the foregoing, reference has been made in particular to the compensation of torsional vibrations, wherein the damping bodies are deformed transversely to the joint axes. But the universal joint according to the invention also offers - as already indicated - the advantage that axial vibrations or shocks can be compensated in the shaft direction. In this context, the invention namely lo further provides that the damping body in the direction orthogonal to the hinge axes are deformable. Thus, the joint body can be subjected to shear loads that lead to the compensation of vibrations or shocks in the direction of the joint forks respectively connected waves. In this point, there is a significant advantage over the initially discussed generic class i5 the technique according to DE 192 89 990 Al, in which only a torsional vibration compensation is provided, but axial vibrations can not be compensated due to the central bolt.

In order to avoid overloading as a result of axial vibrations, 20 provides a development of the invention, that on both sides of the joint part lock washers are arranged, which are connected to each other via an anchor. The lock washers allow deformation of the hinge in the axial direction to some extent. This can be achieved, for example, in that the securing disks are arranged at a distance from the joint part in the direction of a longitudinal axis orthogonal to the joint axes substantially. However, in order to avoid an abrupt impact of individual segments on the lock washers, a further development of the invention provides that the hinge part, preferably each segment of the hinge part, has buffer means on its surfaces facing the lock washers. Thus, in the event of load, the segments set over to the buffer means on the lock washers, the buffer means leading to an additional damping in the axial direction.

An alternative embodiment of the invention provides that the joint part is supported on both sides on a facing inner surface of the yoke in the direction of the longitudinal axis 5 of the joint part. This is particularly advantageous in the range of high speeds occurring, since due to the axial support an axial Reia tivbewegung between the segments and resulting shear loads significantly reduced or completely eliminated.

For this purpose, provision can be made for the joint part to have at least one support on both sides.

5 tel, via which it is supported on the facing inner surface of the respective yoke in the direction of the longitudinal axis. This support means may be formed dome-shaped on a surface facing away from the articulated surface, which is supported on the inner surface of the Geienkgabel. The radius of curvature of the surface of the support means formed as a spherical cap is arranged concentrically to the lo respective joint axis of the adjacent yoke. Due to this design, the yoke can continue to be pivoted relative to the supported joint part on its own joint axis and fulfill the function of a universal joint. In addition to such a punctiform support of the joint part on a yoke, a planar support is also possible in that the inner upper surface of the yoke has a corresponding dome-shaped recess for receiving the dome-shaped surface of the support means. Likewise, a linear support via correspondingly arranged ribs and corresponding recesses on the inner surface of the yoke and the dome-shaped surface of the support means is conceivable. It can along the

O The pivoting direction of the yoke-extending ribs is arranged on one of the two surfaces and accommodated in the depressions on the respective other surface.

Furthermore, it can be provided in this alternative embodiment of the invention, 5 that between the support means and the joint part, an axial damper assembly is arranged. In this case, the axial damper assembly comprise a pre-damper. The pre-damper may be formed substantially disc-shaped. The axial damper arrangement, in particular the pre-damper, can be made of a damping material such as plastic, aluminum or the like and thus allows a high impedance jump, ie energy is consumed or used when a vibration introduced via the yoke from the support means in passes the pre-damper. In this way, initiated by the propeller shafts on the joint forks axial vibrations and shocks significantly attenuated or eliminated. In a further development, the predamper has at least 5 a receiving area for receiving a damping element. By using further damping elements, as with the use of inserts between the two-part damping bodies, the deformation behavior the axiaien damper arrangement admits and in particular a progressive deformation behavior can be achieved.

Another function of a provided with at least two receiving areas 5 predamper can lie in the recording of two segments at their free axial end faces. This is particularly advantageous in the case of two segments connected to a segment pair, since these can thereby be stabilized relative to one another in their relative position.

In addition, the segments can each have at least one recess at their axial end faces. This can achieve a significant material savings. Due to the lower use of material, the weight of the segments or segment pairs is reduced, whereby the moving masses are advantageously reduced in operation of the universal joint. 5

For centering the segment pairs, in a further development of the alternative embodiment of the invention, the joint part may comprise a centering pin. This can be received by a radial bearing in a central region of the joint part relative to this movable. Furthermore, it can be provided that the axial damper arrangement comprises a damping layer, via which the segments of the joint part and the centering pins or the segments and the damping elements are coupled. This can in turn be made of an elastic material, such as rubber. In this way, for example, vibrations occurring from a yoke on the bearing means on a first segment pair

.5 are transmitted, not undamped over the centering pin to the second segment pair.

A development of the invention provides central mounting openings in the joint part. By providing mounting holes, the hinge part can be fixed in the bearing openings, for example when needle roller bearings are attached. so

The invention is explained below by way of example with reference to the accompanying figures. They show:

1 shows a perspective view of a first embodiment of the universal joint according to the invention without a top-side lock washer, FIG. 2 shows a cross section of the universal joint according to the invention according to FIG. 1 along the line H from FIG. 1, FIG.

3 shows a perspective view of the universal joint according to the invention according to FIG. 1 with top-side lock washer,

4 shows a perspective view of the universal joint according to the invention according to FIG. 1 with top-side lock washer in partial section; FIG. 5 is a schematic diagram of a propeller shaft in the steering line of a motor vehicle; FIG.

6 shows a perspective view of a second embodiment variant of the universal joint according to the invention without top-side securing disk;

FIG. 7 shows a cross section of the second embodiment variant according to FIG. 6 similar to FIG. 2; FIG.

8 is a perspective view of the second embodiment of the universal joint according to the invention with top-side lock washer.

! 0

9 is a perspective view of the second embodiment of the universal joint according to the invention with top-side lock washer in partial section.

10 shows a perspective view of a third embodiment of the inventive universal joint according to the invention;

11 shows a longitudinal section of the third embodiment according to FIG. 10;

Fig. 12 is a cross-sectional view of the third embodiment along the line XII-) XII in Fig. 11;

13 shows a cross section through the bearing bush of a possible slide bearing along the line IMI in Figure 2; and

^; 14 shows a cross section through the bearing bush of a possible storage with needle roller bearings along the line III-III in Figure 7. In FIG. 1, a first embodiment of a damped universal joint according to the invention is shown and designated generally by 10. The universal joint 10 comprises an elastic joint part 12 and two joint forks 14 and 16. Via an indicated extension 18 of the joint forks 14 and 16, these can be connected to shafts 74 5.

The elastic joint part 12 essentially comprises two pairs of segments 20 and 30, which are composed of the respectively opposite separately executed segments 22, 24 and 32, 34. The elastic joint part 12 further includes a lo star-shaped damper assembly 50, which is made of an elastic material, preferably rubber, and which mainly serves the torsional damping of the universal joint. The damper assembly 50 has four damper body 51i, 51 ₂ , 5I ₃ and 5U, which are integrally connected to each other via a central connecting ring 53. Each of the damper bodies is 5I ₁ , 5I ₂ , 5I ₃ and 5I ₄ between two

L5 adjacent segments 22, 24 and 32, 34 are arranged and vulcanized to this, so that the damper body 51i, 5I ₂ , 5I ₃ and 5I ₄ each at an approach of two adjacent segments on pressure and in a mutual removal of two adjacent segments to train loaded are.

: o Further, buffer means 60 are provided on the hinge part 12, which are also made of an elastic material, preferably rubber, and contribute to the axial damping. The exact operation will be described with reference to the following figures.

As can be seen in FIG. 2, the joint forks 14, 16 are connected via bearing bolts 26 to the two segment pairs 20, 30. The joint forks 14, 16 each have bearing bores 64 for receiving the bearing pin 26, in which these are screwed or pressed. At the other end, the bearing bolts 26 are inserted into bearing openings 28 of the disc-shaped joint part 12 in a pivot bearing, in

) For example, a needle bearing 42 or a plain bearing recorded.

The bearing openings 28 are introduced into the individual segments 22, 24 and 32, 34, which are made of plastic or metal, for example. In each case two opposite bearing openings 28 are formed substantially coaxially; and define the hinge axes Bl and B2 about which the joint forks 14, 16 can rotate relative to the hinge portion 12. This can be used for cardan shafts typical Zwischenwinkei α between the individual shafts 74, as shown in Hg. 5, implemented.

A sealing surface 36 on the bearing pin 26 also allows the attachment of a 5 sealing ring 38 on the bearing opening 28 of the segments 22, 24 and 32, 34. This ensures that no lubricant can escape from the bearing opening 28, whereby a lifetime lubrication of the bearing pin 26 reaches can be.

In operation, a torque acting, for example, on the drive-side yoke 14 about its longitudinal axis is transmitted to the segment pair 20 via the bearing bolts 26. The output-side yoke 16 opposes a rotation under resistance. As a result, the segment pair 20 is rotated relative to the segment pair 30 about the longitudinal axis A of the joint part 12, which is substantially orthogonal to the two joint axes Bl and B2. The elastic damping bodies 5I ₁ , 5I ₂ , 51 ₃ and 5I ₄ are alternately compressed and stretched by the relative movement of the segment pair 20 relative to the segment pair 30. In the example, the damping body 51i and 5I _{3 are} compressed, whereas the damping body 5I ₂ and 5I ₄ are stretched accordingly. Torsional vibrations are absorbed and damped in this way by the damping bodies 20 51i, 5I ₂ , 5I3 and 5I ₄ .

In terms of magnitude larger torques, the compression-stressed damping body 5I ₁ and 5I _{3 are} deformed so far that the opposite the end faces of the segments 22, 24 and 32, 34 projecting abutment surfaces 46 of the first

Apply 5 pairs of segments 20 on the compression-stressed damping bodies 5I ₁ and 5I3 to the opposing abutment surfaces 46 of the second segment pair 30. Thus, there is a direct transfer of the torque to the second segment pair 30 and from there to the connected yoke 16. This has the advantage that the damping body 51 only compressive forces up to a maximum

0 value, which is defined by the angle ß, which determines the clear gap 48 between the abutment surfaces 46.

The arrangement according to the invention is also adjustable in its damping behavior. By axially changing the position of one or more of the bearing pins 26 5, the segment 22, 24 and 32, 34 connected thereto can be displaced in position relative to the joint center. As a result, with appropriate adjustment of the other segments 22, 24 and 32, 34, a change in the bias voltage the damper assembly 5ö can be achieved. If one of the bearing bolts 26, for example, in the direction of the joint center further screwed into the yoke 14, 16, so also connected to this segment 22, 24 and 32, 34 by the support of the bearing pin 26 on the yoke 14, 16 of the therein stored bearing pin 26 is pressed in the direction of the joint center. This results in a compensating compression of the damping body 5I ₁ , 5I ₂ , 5I ₃ and 5I ₄ between the segments 22, 24 and 32, 34th

The damper assembly 50 is also deformable in the direction along the longitudinal axis A lo, so that in addition to the above-described damping of torsional vibrations and axial vibrations and shocks can be attenuated in the longitudinal direction. In order to avoid a safeguard against overloading of the elastic joint part 12 due to axial loads are on top and bottom of the disk-shaped joint part 12, as shown in Figures 3 and 4, i5 lock washers 52 attached. These are connected to one another via a centrally arranged in the joint part 12 anchor 54 with a defined by a spacer tube 56 distance d from the top and bottom of the joint part 12. Due to the defined distance d, an axial movement of the segments 22, 24 and 32, 34 in the direction of the longitudinal axis A is admitted to a certain extent. However, larger axial movements, which could result in failure of the elastic hinge part 12, are avoided by the lock washers 52 as axial stops for the segments 22, 24 and 32, 34.

On the upper sides of the individual segments 22, 24 and 32, 34, the buffer means »5 60 are mounted, which prevent abrupt abutment of the segments 22, 24 and 32, 34 on the lock washers 52. Upon movement of the segments 22, 24 and 32, 34 in the axial direction towards a lock washer 52, put the buffer means 60, which act even spring on the lock washer 52 and damp the movement.

: 0

Figure 5 shows a classic installation situation, for universal joints. Via a steering wheel 70, a steering torque is applied to a steering shaft 72. This must be transmitted to a steering gear 76 via the steering shafts 74 angled relative to one another at the angle .alpha. The shaft assembly of steering shaft 72 and steering shafts 74 has two 5 universal joints 10 according to the invention. In the following, the second embodiment according to FIGS. 6 to 9 will be discussed. For ease of description and to avoid repetition, the same reference numerals are used for equivalent components as in the description of the first embodiment according to Figures 1-4 and Figure 5 5, but with the number "1" introduced.

The decisive difference between the first and the second embodiment consists in a multi-part damper assembly 150 and an insert cross 159, which is composed of four flat insert parts 158i, 1582, 1583 and 1584. Each insert part 158i, 1582, 158 ₃ and 158 ₄ separates the

Damping body between two adjacent segments 122, 124 and 132, 134 respectively in two damping body halves 151a and 151b. Thus, four damping bodies 151i, 15I ₂ , 151 ₃ and 15I _{4 result} , which are composed of the damping body halves 151χa / b, lδha / b, 15l ₃ a / b and 151 ₄ a / b. Each insert part 158i, 158 ₂ , 158 ₃ and 158 ₄ is designed to be longer in the radial direction than the damping bodies 15I ₁ , 15I ₂ , 15I ₃ and 151 ₄ . There are gaps 148 between the adjacent segments 122, 124 and 132, 134.

In this way, with different stiffnesses of the insert cross 159 and .o the damping body 151i, 15I ₂ , 15I ₃ and 151 ₄ a two-stage damping can be achieved: In a first deformation phase, ie at lower torques, are essentially only the softer damping body 151i, 15I ₂ , 15I ₃ and 15I ₄ deformed. As the torque increases, the deformation of the softer damper bodies 151i, 15I ₂ , 15I ₃ and 15I ₄ progresses until the inlay cross 159 i5 abuts abutment surfaces 146 of adjacent segments 122, 124 and 132, 134. The damping takes place until then significantly on the damping body 151i, 15I ₂ , 15I ₃ and 15I. ₄ In a second deformation phase takes against the damping body 151i, 15I ₂ , 15I ₃ and 15I ₄ stiffer deposit cross 159, which is already on the abutment surfaces 146 of the segments 122, 124 and 132, 134 on 0, the torque alone attenuating. The damping bodies 15I ₁ , 15I ₂ , 15I ₃ and 15I ₄ are short-circuited.

A characteristic corresponding to this arrangement for the spring stiffness has a progressive course with a kink at the point at which it comes to a concern 5 of the insert cross 159 at abutment surfaces 146. An adjustment by selecting different material combinations of the damping body 15I ₁ , 15I ₂ , 151 ₃ and 151 ₄ and the deposit cross 159, as well as the use of multiple inserts is also conceivable.

The insert cross 159 also assumes the function of the spacer tube 56 of the joint part 12 according to the first embodiment in this embodiment of the invention. This is because it also protrudes beyond the segments 122, 124 and 132, 134 and damping body 151 in terms of its width in the direction of the longitudinal axis A. The distance d of the lock washers 152 is thus not defined by means of the spacer tube 56, but by means of the axially projecting insert cross 159th

The holes 162 shown in Figures 6-9 are for decoupling and supporting the segments 122, 124; 132, 134 provided during assembly of the needle bearings 142.

In the following, the third embodiment according to FIGS. 10 to 12 will be discussed. For ease of description and to avoid repetition, the same reference numerals are used for equivalent components as in the description of the first embodiment according to Figures 1-4 and Figure 5, but with the number "2" introduced.

In contrast to the first and second embodiments of the invention already described, the embodiment of a universal joint 210 according to the invention shown in FIGS. 10 to 12 has an axial support of the joint part 212 on the two joint forks 214 and 216. The segments 222, 224; 232, 234 are connected in this embodiment to segment pairs 220, 230, which are supported on both sides via an axial damper arrangement 286 and a support element 284 on the inner surfaces 282 of the two joint forks 214 and 216. Each segment pair 220, 230 comprises two opposing segments 222, 224 and 232, 234 of the joint part 212 and a connecting element in the form of a carrier plate 225, 235, which connects the segments 222, 224 and 232, 234 on one end face.

Between the segments 222, 224; 232, 234 extends in the direction of the longitudinal axis A a central through hole 245 described in more detail below for receiving a cylindrical centering pin 294. The carrier plates 225, 235 have in addition to this central through hole 245 receptacles 255i and 255 ₂ and openings 265. The recordings 255i and 255 ₂ serve, as can be seen in FIG Recording additional damping elements 292, which - shown in longitudinal section - are cup-shaped and the free end surfaces of the segment pair 220, 230 connected segments 222, 224; 232, 234 record. In this way, the segments 222, 224; 232, 234 stabilized at their free ends in their relative s position to each other. The damping elements 292 also allow an exact adjustment of the deformation behavior of the entire axial damper assembly 286, in particular the setting of a progressive deformation.

In order to ensure the function of the universal joint, namely the pivotability of the joint gaels 214 and 216 with respect to their respective joint axes B1 and B2, the support part 284 is dome-shaped on its surface facing the yoke, i. shaped like a ball segment cut with a plane. The adjacent inner surface 282 of the joint forks 214 and 216 is provided in correspondence with a dome-shaped recess for receiving the dome-shaped surface of the support means 284. As an alternative to such a planar support of the support element 284 with respect to the inner surface 282 of the joint forks 214 and 216, as already mentioned above, a linear, for example with the aid of ribs and possibly these receiving recesses or a punctiform support is conceivable.

> 0

The axial damper assembly 286 includes a pre-damper 288 that is substantially disc-shaped. In addition, on the left side of the arrangement in FIG. 11, a damping insert 290 is provided between the damping elements 292 accommodating the free end faces of the segments of a first segment pair 220 and the carrier plate 235 of a second segment pair 230. These damping inserts 290 are also formed in the form of a shell in longitudinal section and connected to the disk-shaped predamper 288 via the openings 265 of the support plate 235 of the second segment pair 230. In addition, the damper assembly 288 shown in FIG. 11 includes a damping layer 275.

0 on the pairs of segments 220, 230 in the region of the central passage opening 285 and the free end faces of the segments 222, 224; 232, 234 is present. This is made of an elastic material, such as rubber.

The segments 222, 224; 232, 234 of the two segment pairs 220, 230 are, as

1 already described in the above embodiment, via bearing pin 226 and needle bearing 242 connected to the joint forks 214 and 216. Furthermore, the segment pairs 220, 230 in this third embodiment of the invention over the Bearing pin 226 axially biased against the respective inner surface 282 of the joint forks 214 and 216, respectively. For this purpose, during assembly of the universal joint 210, the individual segment pairs 220, 230 of the joint part 212 against the damper assembly 288 and the respective support element 284 in the direction of the supporting joint

5 fork 214 or 216 pressed to bring the openings 228 for receiving the bearing pin 226 in register with the bearing bores 264 on the respective yoke 214 and 216, respectively. As a result of this axial prestress, the deformation behavior of the damper arrangement 286 arranged between the segment pairs 220, 230 and the joint forks 214 and 216 is adapted and a progressive identification in the axial direction of loading is achieved. In addition, the axial preload ensures an immediate response of the axial damper assembly 286.

Another feature of the third embodiment according to FIGS. 10 to 12 is shown in particular in FIG. Instead of an armature for fixing securing shims, as in the embodiments described above, this is

Embodiment, a centering pin 294 is provided, which is mounted relative to the individual segments of the segment pairs 220, 230 via a radial bearing 296 movable. The radial bearing 296 is supported on its outer circumferential surface in addition to the damping layer 275 of the segments from which a transmission of

20 vibrations significantly dampens or prevents. In this way, vibrations that are transmitted via a first yoke 216 and bearing pin 226 on the segments of a first segment pair 230 is not or only significantly attenuated via the centering pin 294 and the radial bearing 296 on the second segment pair 220 and the associated steering fork 214 become.

! 5

Furthermore, the third embodiment, in contrast to the embodiments 1 and 2 of Fig.l to 9 in a region of the end faces of the segments has a concave curvature 280. The two-part damping body 251i a / b; 25I ₂ a / b, 25I3 a / b and 25I ₄ a / b, which as in the previous embodiments to the

0 end faces of the segments are vulcanized, thus have in this area on a collection of material. This in turn enables an improved progressive deformation behavior of the damping bodies 25I ₁ , 25I ₂ , 25I ₃ and 25I ₄ . An additional insert cross may be provided as in the other embodiments between the damping bodies. However, in the third case,

5 tion form of the invention, a short circuit, ie an undamped transmission of vibrations, two adjacent segments directly via corresponding abutment surfaces (as in the first embodiment of Figures 1 to 4) or via the insert part (as in the second embodiment of FIG. 6 to 9) not desired.

The peculiarity of this third embodiment of the invention is namely 5 _. In particular, in that over the entire rotation angle range of the universal joint 210 no vibrations, that is, neither axial vibrations nor radial vibrations, are unattenuated by a yoke 214 or 216 transmitted to the other yoke 216 or 214. In this case, the axial vibrations are attenuated substantially via the damper arrangement 286, while the radial lo vibrations or torsional vibrations are substantially damped via the damping bodies 25I ₁ , 25I ₂ , 25I ₃ , 25I ₄ . All metallic parts of the joint assembly according to this embodiment of the invention are decoupled from each other by damping elements of the damper assembly 286 and the damping body 25I ₁ , 25I ₂ , 251 ₃ , 251 ₄ .

15

Another advantage of this third embodiment of the invention is that, in particular under torsion and simultaneous flexion angle of the joint 210 no shear stress of the joint part 212 due to axial vibrations occurs because the hinge part 212 through the bearing pin 226 via the damper assembly 286 and

20 supporting elements 284 is biased against the two joint forks 214 and 216 dampening. In addition, the damper assembly 286 and the support members 284 are exposed due to the axial bias against the joint forks 214 and 216 in the axial direction only compressive stresses, whereby the life of the joint part is advantageously influenced over conventional solutions.

»5

The damper assembly 286 of a pair of segments 220 and 230 is integrally connected with this in Fig. 11 and 12 embodiment with the damping bodies 251-j _b, 251i _a, 251 ₂ b, 25l3a and 251 ^ 251 _2a, _25l3t>, 25uA , The corresponding parts of the joint part 212 are placed for this purpose in a mold and with a

10 molded rubber material. In a subsequent step, the rubber material is vulcanized and connects in this way the individual parts of the joint part 212.

The entire universal joint is additionally provided in FIGS. 10 to 12 with a protective jacket 298. 5

Further advantages, which are already known from the first two embodiments of the invention, can also be found in this embodiment. In FIGS. 13 and 14, two different embodiments for the rotatable mounting of the bearing bolts 26 in the segment 22 are shown representatively for all the segments 22, 24 and 32, 34. In the first embodiment according to Figure 13, the bearing pin 26 is enclosed by a bearing bush 40 and forms with it a sliding bearing. The bushing 40, here designed as a collar bush, can be pressed into the bearing opening 28 or be produced by means of two-component injection molding! If the segments 22, 24 and 32, 34 made of a suitable material, such as plastic, the bearing bush 40 may also be omitted, but then 28 lubrication grooves 44 must be provided in the bearing opening.

In the second embodiment according to Figure 14, the rotatable mounting of the bearing pin 26 is implemented by a needle bearing 42, wherein to ensure an improved bearing pressure grooves 144 are provided on the circumference of the bearing opening 28.

Claims

claims

5 1. Universal joint (10) for connecting torque transmitting shafts, in particular for steering spindles (72) and propeller shafts of motor vehicles, with two joint forks (14, 16), which are each connected to a shaft and each having a pair of bearing means, one between the Jointed parts (14, 16) arranged joint part (12) with lo two pair of complementary bearing means which define two mutually crossing or skewed joint axes (Bi, B ₂ ), and at least one torsional vibration damping, in the joint part (12) arranged damper assembly (50) wherein the two joint forks (14, 16) are coupled to one another by the paired cooperation of the bearing means and complementary bearing means via the joint part (12), characterized in that the joint part (12) comprises two segment pairs (20, 30), each of which segment (22, 24 and 32, 34) is formed separately and connected to a respective complementary bearing means, and that in each case two adjacent segments (22, 24 and 32, 34) via in the direction transverse to the hinge axes (Bi, B ₂ ) deformable damping body (51i, 5I ₂ , 5I ₃ , 5I ₄ ) of the damper assembly (50) are coupled together.

2. Cardan joint (210)) for connecting torque transmitting shafts, 5 in particular for steering spindles (72) and propeller shafts of motor vehicles, with two joint forks (214, 216), which are each connected to a shaft and each having a pair of bearing means, one between the joint forks (214, 216) arranged joint part (212) with two pairs of complementary bearing means defining two intersecting or 0 skewed joint axes (Bi, B ₂ ), and at least one torsional vibration damping, in the joint part (212) arranged damper assembly (250 ), wherein the two joint forks (214, 216) are coupled to one another via the joint part (212) by pairwise cooperation of the bearing means and complementary bearing means, characterized in that the joint part (212) comprises two segment pairs (220, 230) each having two segments (222, 224 and 232, 234) over at least one connecting element are connected to each other, wherein each segment (222, 224 and 232, 234) is respectively connected to a complementary bearing means, and that in each case two adjacent segments (222, 224 and 232, 234) in the direction transverse to the hinge axes (Bi, B ₂ ) deformable damping body 5 (25 Ii, 251 ₂ , 25I ₃ , 25I ₄ ) of the damper assembly (250) are coupled together.

3. Cardan joint (10) according to claim 1 or 2, characterized in that each of the bearing means comprises a bearing pin (26) and each of the complementary bearing means each having a bearing pin (26) receiving 10 mende bearing opening (28), wherein the bearing opening (28) preferably in a bearing bush (40) or in a rolling element bearing (42) received in a segment (22, 24 and 32, 34) and formed, for example, with lubrication grooves (44) and the bearing pin (26) preferably has a sealing surface (36) for sealing the bearing opening (28). 5

4. universal joint (10) according to claim 3, characterized in that the bearing pin (26) variable in the yoke (14, 16) can be introduced, wherein in accordance with the position of the bearing pin (26) in the yoke (14, 16) Damper assembly (50) of the joint part (12) prestressable »0 is.

5. Cardan joint (10) according to any one of the preceding claims, characterized in that the hinge part (12) is disc-shaped and divided into at least four segments (22, 24 and 32, 34), wherein between einan- 5 of the opposite end faces of two adjacent Segments (22, 24 and 32, 34) at least one damping body (51i, 5h, 5I ₃ , 5I ₄ ) is arranged, wherein the damping body (51i, 5I ₂ , 5I ₃ , 5I ₄ ) in particular of an elastic material, preferably made of Rubber, prepared and preferably vulcanized to the end faces of the segments (22, 24 and 32, 34).

6. universal joint (10) according to claim 5, characterized in that the damping body (51i, 5I ₂ , 5I ₃ , 5I ₄ ) are interconnected and / or) in the direction orthogonal to the joint axes (Bi, B ₂ ) are deformable.

7. Cardan joint (10) according to any one of the preceding claims, characterized in that the segments (22, 24 and 32, 34) relative to their Stim surfaces raised abutment surfaces (46) and / or in a region of the end faces have a concave curvature (280).

8. universal joint (10) according to any one of the preceding claims, characterized in that between two mutually opposite end surfaces of two adjacent segments (22, 24 and 32, 34) provided in each case a flat insert portion (158i, 158 _2, 158 _3/158 ₄₎ , and that the insert portion (158i, 158 _2/1583, 1584) via a respective damping body (51i, 5I _2, 5I3, 5U) is connected to the facing it faces, wherein the insert portion (158i, 158 _2, 158 _3, 1584) and the damping bodies (51i, 51 _{2 /} 5I ₃ , 5I ₄ ) preferably have different stiffnesses.

9. universal joint (10) according to claim 8, characterized in that between the segments (22, 24 and 32, 34) arranged insert parts (158i, 158 ₂ , 158 ₃ , 1584), preferably to an insert cross (159), in one piece connected to each other.

10. universal joint (10) according to any one of the preceding claims, characterized in that on both sides of the joint part (12) locking washers (52) are provided which are connected via an armature (54) and preferably in the direction of one of the joint axes (Bi, B ₂ ) substantially orthogonal longitudinal axis (A) at a distance (d) to the hinge part (12) are arranged.

11. universal joint (10) according to claim 10, characterized in that the hinge part (12), preferably each segment (22, 24 and 32, 34) of the joint part (12), at its the locking washers (52) respectively facing surfaces buffer means ( 60).

12. universal joint (210) according to one of claims 1 to 9, characterized in that the hinge part (212), preferably each segment (222, 224 and 232, 234) or segment pair (220, 230), on both sides, in particular via at least one support means (284), on a facing inner surface (282) of the yoke (214, 216) in the direction of the longitudinal axis A is supported, wherein the support means (284), for example, on a side remote from the hinge part (212) side, which abuts the inner surface (282) of the yoke (212, 214) is supported, is formed dome-shaped.

13. universal joint (210) according to claim 12, characterized in that between the support means (284) and the joint part (212) an axial damper assembly (286) is mounted, which for example comprises a pre-damper (288), which is preferably substantially disc-shaped - 5 is formed and / or at least one receiving area (290) for receiving at least one damping element (292).

14. universal joint (10) according to claim 12 or 13, characterized in that the hinge part (212) umlo loosely a centering pin (294), preferably via at least one radial bearing (296) relatively movable to the segments (222, 224 and 232, 234) is received in a central region of the hinge part (212).

15. Universal joint (10) according to claim 13 or 14, characterized in that the axial damper arrangement (286) comprises a damping L5 layer (297), via which the segments (222, 224 and 232, 234) of the joint part (212). and the centering bolt (294) and the segments (222, 224 and 232, 234) and the damping elements (292) are coupled.

16. Universal joint (10) according to one of the preceding claims, marked • o net by central mounting holes (162) in the joint part (12).

70/7541